Apparatus for high-speed cutting of cylindrical metal members



Nov. 25, 1952 o. A. NEALE 2,619,174

APPARATUS FOR HIGH-SPEED CUTTING OF CYLINDRICAL METAL MEMBERS Fil ed Feb. 26, 1949 4 Sheets-Sheet 1 F l a I INVENTOR OLIVER A/VE/ILE ATTORNEY Nov. 25, 1952 o. A. NEALE 2,619,174

APPARATUS FOR HIGH-SPEED CUTTING OF CYLINDRICAL METAL MEMBERS Filed Feb. 26, 1949 4 Sheets-Sheet 2 INVENTOR OL/VER A. NEALE ATTORNEY Nov. 25, 1952 o. A. NEALE 2,619,174

APPARATUS FOR HIGH-SPEED CUTTING OF CYLINDRICAL METAL MEMBERS Filed Feb. 26, 1949 4 Sheets-Sheet s gal A INVENTOR 1 5 Ouvm 14. NEALE ATTORNEY Patented Nov. 25, 1952 UNITED STATES ATENT OFFICE APEARATUS FOR HIGH-SPEED CUTTING OF GYLINDRICAL METAL MEMBERS Application February 28, 1949, Serial No. 78,484

13 Claims.

This invention relates to high speed metal cutting apparatus and, more particularly, to such apparatu for severing sections from cylindrical metal membtrs, such as tubes and pipes for example.

Various arrangements have been used or proposed for cutting cylindrical metal work members to predetermined lengths. For example, machines have been used which rotate the workpiece in engagement with a fixed tool. Such machines have not been satisfactory for use in the production line cutting of steel tubing, for example, and it has been proposed in such applications to hold the work against rotation and revolve the tools around the work.

The revolving tools exert a centrifugal force proportional to their mass and the square of their velocity. To force the tools to out into the work, much effort is required to overcome the centrifugal force, which means an uneconomical use of power in the cutting operation. Consequently, attempts have been made to balance the centrifugal force of the revolving tools by springs or the like, but these attempts have not been satisfactory from the practical standpoint.

Another factor which has hindered the development of high speed rotary cutting apparatus is the problem of balancing the tools at high speeds. Even a slight static unbalance of the tools is greatly magnified when the tools are rapidly revolved. The unbalancing detracts from the accuracy of the cut, so that it is difii cult to cut successive tube sections, for example, to the same length within close tolerances. Additionally, in prior art machines of the revolving cutter type, the stability has been deleteriously afiected by the location of the radial thrust support at a substantial distance from the tool pressure point. The foregoing deficiencies in prior art cutting machines have prevented full advantage being taken of the production line cutting possibilities of high speed cutting tools.

In contrast, the apparatus of the present invention includes a hollow stationary spindle having a tool carrying head rotatably mounted thereon. The tools are slidably mounted on the forward face of the head for substantially radial reciprocation toward and away from the work and each tool is linked, as by a bell crank, to a counterweight slidably mounted for radial movement in the head in relatively close axially spaced relation to the tool. Due to the interconnecting linkages, and as the counterweights have masses substantially equal to those of the tools and their supports, the counterweights substantially balance the centrifugal force of the tools and supports. Consequently the force required to engage the tools with the work is only the net force required to bite the tools into the work. This force is exerted by an axially movable feed ring engaged with the bell cranks. Advance of the feed ring moves the tools toward the Work and retraction of the ring positively retracts the tools from the work.

Within the hollow stationary spindle is mounted a collet chuck comprising substantially telescoped inner and outer non-rotatable cylindrical collets. The inner collet is longitudinally fixed and receives the member to be cut, its fixed position contributing to the accuracy of setting the member with respect to the tools to assure cutting to a predetermined length. The outer collet is longitudinally movable to clamp the inner collet against the work member.

Such clamping of the Work member is effected at a zone immediately adjacent the pressure point of th tools, and in radial alignment with a radial bearing rotatably supporting the cutting head on the fixed hollow spindle, this hearing being axially intermediate the tools and the counterweights. Thus, effective rigid support for the revolving tools is provided at a zone immediately adjacent the tool pressure point. This enhances the rotational stability for the cutting head, contributing substantially to the accuracy of the cut.

A feature of the invention is the location of the carbide tipped cutting tools for movement in two axially spaced radial planes. With this arrangement, a sample ring may be cut from a tube at the same time as the latter is being cut to a predetermined length. Quite a few customers require such sample rings from one or both ends of a tube length.

The operation of the apparatus is fully automatic once it has been manually initiated by depressing a start push button. With the tube accurately positioned in the inner stationary collet, the outer collet is automatically drawn longitudinally to clamp the tube. At the limit of clamping, the tools are rapidly moved toward the work and then moved inwardly at a controlled rate to make the out. At the end of a predetermined depth of cut, the tools are automatically and positively retracted and the collet chuck is automatically released, completing the operational sequence.

With the foregoing in mind, it is an object of this invention to provide an eficient high speed 3 cutting apparatus for cylindrical members such as metal tubes.

Another object is to provide such an apparatus including fully mass counter-balanced revolving cutting tools having carbide tips.

A further object is to provide such an apparatus including a. stationary hollow suporting spindle rotatably supporting a cutting head and having a non-rotatable collet chuck therein, including a fixed tube-positioning collet.

Still another object is to provide such an apparatus including rigid support for the cutting head at a zone immediately adjacent the tool pressure point and at the point of clamping the work in the collet chuck.

Yet another object is to provide such an apparatus in which the operational sequence is automatically performed responsive to a manual initiation.

These and other objects, advantages, and novel features of the invention will be apparent from the following description and the accompanying drawings. In the drawings:

Fig. 1 is an axial sectional view through cutting apparatus embodying the invention, with the lower half of the figure showing the tool feeding means in advanced position and the upper half showing such means retracted;

Fig. 2 is a front elevation view of the apparatus, showing the feeding means in the two positions as in Fig. 1;

Fig. 3 is a partial top plan view of the forward end of the apparatus, with the feed ring removed;

Fig. 4 is a radial sectional view of the apparatus on the line 4-4 of Fig. 1, looking in the direction of the arrows;

Fig. 5 is a partial horizontal sectional view of the apparatus on the line 55 of Fig. 1; and

Fig. 6 is a schematic diagram illustrating an automatic control system for the apparatus.

Referring to Fig. 1, the cutting apparatus includes a stationary hollow supporting spindle l which is mounted, at its rear end, in a fixed support H and held against rotation by a key I2. A non-rotatable, longitudinally movable substantially cylindrical collet I is mounted within spindle l0, and slidably bears within a guide ring |3 at the forward end of spindle l0 and an annular inner shoulder |4 near the rear end of the spindle. Between ring l3 and shoulder l4, and

. rearwardly of the latter, collet I5 is spaced from spindle III to reduce frictional resistance.

The forward end of collet I5 is longitudinally slotted and gradually reduced in inner diameter to form a series of circumferentially spaced, wedge fingers I6 having sloping inner surfaces These fingers overlap and cooperate with the outer sloping surfaces 22 of thickened wedge fingers 2| formed in the forward end of a non-rotatable, longitudinally stationary and substantially cylindrical inner collet 2D. The latter is mounted within and in radially spaced relation to collet l5, so that the two collets are telescopically associated although not in surface engagement with each other except at their fingers when clamped on a workpiece. It should be noted that the outer surfaces I8 of fingers |6 are parallel to and engage the inner surface of ring |3.

The inner surfaces 23 of fingers 2| are substantially parallel to the inner surface of ring l3 and also to the outer surface of a cylindrical metal work member, such as tube 25. It will be seen that, when movable collet I5 is drawn to the right as viewed in Fig. 1, fingers It will wedge fingers 2| against tube 25 to clamp the latter in longitudinally fixed, non-rotatable relation. The fixed inner collet 20 provides for accurate presetting of tube 25 with relation to the cutting head, so that the tube may be cut accurately to a predetermined length, or annular sections of an accurately predetermined length may be cut from the tube. The uniform clamping action is facilitated by the circumferentially relatively staggered relation of fingers l6 and 2| (see Figs. 1 and 2), with each finger I6 overlapping two adjacent fingers 2|. The arrangement of collets l5 and 20 forms what may be called a collet chuck, which term will be used hereinafter to designate these two collets jointly.

Stationary spindle ID has a forward outer bearing surface 26 and a second outer bearing surface 21 immediately forward of key |2, and these bearing surfaces carry anti-friction bearings 2'8 and 29, respectively, supporting rotatable cutter head 30 on spindle l0. Head 30 has a forward radial flange 3| embracing bearing 29 and, rearwardly of flange 3|, has a radially enlarged elongated recess 32 forming, with flange 3|, a forward recess receiving a guide ring 35 seated against the outer race of bearing 28, and described more in detail hereinafter. A spacer sleeve 33 abuts ring 35 and the outer race of bearing 29, the inner race of this bearin seating against a shoulder 24 on spindle In to properly position head 30 on the spindle. A back plate 34, secured to head 30, holds the outer race of bearing 29 against sleeve 33, and the inner race is engaged by a clamp ring 36 held in position on spindle 10 by a lock nut 31. The latter is engaged by support I, and spindle H) is locked against axial movement in the support by a lock nut 38 and a lock washer 39. Head 30 may be easily removed from spindle H), for inspection, repair, or replacement by disengaging cap screws 4| which secure plate 34 to head 30. Suitable bearing seals and seal rings are provided as indicated.

Head 30 has a rearward cylindrical sleeve section 42 embracing ring 35, space 33 and bearing 29, and section 42 has its external surface formed with V-grooves 43 to .provide a multiple V-gro'ove belt driven pulley. The forward section 44 of head 30 is likewise cylindrical to form a bearing surface for a feed ring 40, and section 44 is somewhat larger in diameter than section 42. The forward face 45 of head 30 has a discontinuous circular rim 46 (Fig. 2) bounding an axially extending recess 41 of substantial depth.

The forward face 45 of head 30 acts as a mounting support for the reciprocable cutting tools which, in the present case comprise carbide cutting tips or blocks 95, For this purpose, face '45 has secured thereto, on opposite sides of its axis, shoes 5|, 5| which slidably support reciprocable tool holders 5D, 50' on which tips 95, 95' are mounted. Each tool holder is connected by linkage, including bell cranks '65, 65, to counterweights 69, 60, each mounted for reciprocation in radially aligned pockets in ring 35 and head 30. The bell cranks are pivoted on head 30 for swinging movement in an axial plane so as to effect relative reverse radial movement between each tool holder and its connected counterweight. The feed ring 40 is engaged with the bell cranks, to swing the latter to reciprocate the tool holders and their connected counterweight, in a manner described hereinafter.

More specifically, forward face 45 has two relatively deep grooves 48, 48, preferably rectangular in cross section, which are on opposite sides of the center of the plate and parallel to a diameter of the face, but centered equal distances to opposite side of such diameter. These grooves act as seating recesses for fixedly mounting the shoes 5 I, 5I which slidably support the reciprocable tool holders 59, 59'. Shoes 5|, 5| are channel shape in cross section and have slots 52, 52 extending centrally along th inner surfaces of flanges 53, 53 for a purpose to be described.

A pair of radial slots 54, 54 are cut through the periphery of section 44 and aligned with the opposite ends of the aforementioned diameter of face 45. Slots 54, 54 intersect grooves 48, 48 at their forward ends and intersect rectangular radial pockets 59, 59 at their rearward ends, extending beyond pockets 59 to the rear surface of section 44. ,Pocket 59, 56 are diametrically aligned with and form continuations of rectangular radial pockets 51, 51 in guide ring 35 to receive the counterweights 99, 99.

A pair of spaced circumferential slots 59, 59 (Fig. 3) extend toward each radial slot 54 so as form ears 9|, 6! on each side of a slot 54 bored to receive hinge pins 62, 62 each oscillatably mounting a bell crank 95 having forked arms 69, 91. The forked end of each rear arm 99 carries a pin 99 which seat in the forked arms I2 of a link I3. Intermediate arms I2, each pin 98 carries a roller 75 engaging feed ring 49. The opposite end of each link I3 receives a pin I4 mounted in the forked outer end of counterweight 99. These latter are rectangular in cross section to move inwardly and outwardly in radially aligned pockets 59, 51, and the inner ends I9 of the counterweights are arcuate so as to have clearance over a cylindrical sealing ring 11, on the inner surface of guide ring 35 and sealing the inner ends of pocket 5?.

Tool holder 59 comprises an elongated rectangular body portion 3| having rectangular ribs 82 extending along a pair of opposite sides 83 and slidably received in opposing grooves 52 of a shoe 5I. At its outer end, tool holder 59 has a pair of spaced arms 94 carrying a in 86 received in the inner end of a link 95 having forked arms 88. Arms 88 carry a pin 9 I mounted in the forked arm 51 of a bell crank 65. A roller bearing 99 is mounted between each pair of arm 88 and is engaged by feed ring 49 as described hereinafter.

The radially inner front face of holder 59 carries a forwardly projecting elongated rib 92 adjacent which is a shallow rectangular recess 93. The tool 94 is set in recess 93 and against rib 92, having its outer end receiving a pin 96 in the recess and being held in proper alignment by a screw 97. The inner work facing corner of tool 94 carries a suitable carbide cutting tip 95, which is cemented or otherwise held in place.

Tool holder 59' is, in most respects, identical to holder 59, and corresponding parts have been given the same reference numerals primed. However, its inner forward face carries an axially extended portion 93 so that its axial thickness is about to /6 inch more than that of holder 59. This offset carries rib 92' and recess 93' seating tool 94'. The result is that the cutting tip 95' is axially ofiset about /2 inch to inch beyond tip 95 so that, in operation of the apparatus, a 1

sample ring of such width is cut from the tube 25 at the same time as the tube end is trimmed. It will be noted that the forward corners of cutting tips 95, 95' lie in a common axial plane of the work.

With the apparatus as so far described, and with counterweights 99 having substantially the same mass as the tools and tool holders, the counterweights will balance the centrifugal force of the tools and tool holders when head 39 is rotated. Thus, to feed tools 94, 94' inwardly, the amount of force necessary is decreased by the amount of the centrifugal force normally exerted by the tools and tool holders. In other words, the only force required is that necessary to cause bits 95, 95 to cut into tube 25. Furthermore, cutting tips 95, 95', due to the axial extension of tool holder 59', are axially spaced so as to cut a ring from tube 25 as well as to cut the tube to size.

The means for exerting such force comprises the feed ring 49, which is rectangular in cross section and has an inner surface I 9| slidably engaging the outer surface of section 44 of ring 39. Keys I92 constrain feed ring 49 to rotate with ring 39. Ring 49 has a pair of diametrically aligned slots I93, I93 in it inner surface, each slot being substantially rectangular in cross section and aligned with a bell crank 65 whose arms extend outwardly into the slot. Intermediate the ends of each slot I93 is a radially inwardly directed cam I94, illustrated in Fig. 1 as being triangular in axial cross section and centered relative to a circumferential channel I95 in the outer surface of ring 99. In the present instance, the apex angle of each triangular cam I94 is and the sides of the cam carry wear plates I95, I each continuously engaging a roller I5 or 99. Thus, as ring 49 is moved axially, cam wear surfaces I99 move rollers I5 or 99 to swing bell cranks 95 to advance or retract holders 59, 59' and tools 99, 94, and effect radially reversed movement of counterweights 69, 99. It should be understood that, while only a pair of counterbalanced tools have been described, mor than two may be used if necessary or desirable, all of the tools being so angularly related on face 45 that dynamic balance of head 39 is attained.

The operation of the apparatus will be understood best by reference to Fig. 6 which schematically illustrates the hydraulic and electrical control system. Head 39 is rotated from a suitable power source through the medium of one or more multiple V-belts engaging grooves 43, and collet chuck i5, 29 is normally in the position shown in the upper half of Fig. 1. With the collet chuck so arranged, tube 25 is placed in the apparatus and accurately positioned by reference to the forward end of stationary collet 29.

As schematically shown in Fig. 6, inner, stationary collet 29 is locked against longitudinal and transverse movement by securement in a fixed support III which may comprise part of support II of Fig. 1. Outer, longitudinally movable collet I 5 may have the forked end of a lever I96 connected thereto by pins I91, lever I 95 being pivotally secured to a fixed surface as at I98. The rod of a piston I99 of a hydraulic cylinder H9 is connected to an intermediate point of lever I95 so that, when piston I99 moves to the right, the collet chuck is clamped onto tube 25 to hold the latter in fixed position as shown in the lower half of Fig. 1. When piston I99 moves to the left, the

collet chuck releases tube 25 for Withdrawal from the apparatus.

Feed ring 49 is moved axially by a lever I I2, which is pivoted to a fixed surface at H3 and may have a ring or fork carrying rollers H4 engaged in external channel groove I95 of feed ring 49. The rod of a piston IIB of a'hydraulic cylinder H is secured to lever I I2 beyond groove I05. As piston IIG moves to the left, feed ring 40 is moved axially to swing bell cranks 65 to feed the tools toward the work and, as piston I'I5 moves to the right, feed ring 40 is moved axially to swing bell cranks 65 to withdraw the tools from the work.

The feeding of the tools toward the work is effected automatically in response to clamping of tube 25 in the collet chuck, and at a predetermined rate and in a, presett-able amount. Likewise, the tools are automatically withdrawn and the collet chuck automatically disengaged in response to completion of the desired out. For this purpose, a link I I1 connects the free end of lever I I2 to a rod I I8 secured to a longitudinally movable operator I20. The latter has a bevelled forward edge I2I for controlling the operator I22 ofa shut-off valve I25.

Operator I20 also controls the operation of a double throw limit switch I30. For this purpose, operator I20 carries a longitudinally adjustable rod or plate I23 which, as operator I20 moves to the left, engages switch handle I3I to close switch I30. When operator I20 moves to the right, switch handle I3I is reversed, to open switch I30, by an abutment I24 adjustably mounted on the forward end of rod I I8.

The control system further includes an adjustable feed control valve I35 in shunt relation with shut-off valve I25, and sequence valves I40, I45 which receive fluid under pressure from 'a 4-way valve I50 operated by a solenoid I'5I controlled by a push button I52, and a solenoid I53 controlled by limit switch I30. Hydraulic fluid is delivered to valve I50 from a reservoir I25 by a pump I21 driven by a motor I28. Fluid is returned to reservoir I25 through a return line I 5| connected to valves I25, I40, I45 and I50. System pressure is controlled by a pressure regulator I32.

The several valves I25, I35, I40, I45 and I50 are standard, commercially available valves. Shut-oil valve I25 provides for free flow of fluid from left port I33 to right port I34 as long as operator I 22 is not depressed. When operator I22 is engaged by edge I2I, valve I25 shuts off flow of fluid from left to right. This valve also provides for free flow of fluid from right port I34 to return line I3I through port -I36. Valve I35 is "a throttling valve for controllably governing the rate of fluid flow therethrough. Sequence valves I40, I45 are set at a pressure lower than the system pressure and, until the set pressure is exceeded, deliver fluid to their respective side ports I31, I38. When the pressure exceeds the setting of the valves, fluid is delivered to the respective front ports I4I, I42.

With the described arrangement, and with tube 25 located in collet 20 as described, the driving means (not shown) for cutter ring 30 is energized't-o rotate the latter, and push button switch I52 is closed. This energizes solenoid I-5I to move valve I50 to a position delivering fluid under pressure to sequence valve I40 and 'exhausting fluid from sequence valve I45. Valve I40 delivers fluid to the left end of cylinder 1 I0, causing piston I09 to move to the right drawing collet I5 to the right relative to stationary-collet 20. Teeth I5 wedge teeth 2| against tube 25 to clamp tube 25 in a fixed position. When piston I09 can move no further to the --right, as when the collet chuck-is-fully engagedpressure: builds up 'above the pre-set value in valve I40 7 causing this valve to shift its delivery to front port I.

The hydraulic fluid now flows from port III freely through shut-off valve I25 to the right end of cylinder I I5. Piston II5 moves relatively rapidly to the left, causing lever M2 to swin! clockwise and move feed ring and operator I20 to the left. Ring 40 swings bell cranks 65 to move the tools inwardly toward tube 25 but, before the tools are fully engaged with the work, beveled surface III of operator I20 depresses handle I22 of valve I25 to shut this valve. The fluid must now flow at a controlled rate through feed rate control valve I35, which may be set for the desired rate of ieed.

The tool feed into the work continues at the controlled pre-set rate until .plate or rod I23 strikes switch handle I3 I. This action Is adjustable, to pre-"set the depth of the cut, by adjusting rod or plate I23 longitudinally of operator I20. When handle I3I is so operated, switch I30 is closed to energize solenoid I53 to move valve I50 to a position connecting sequence valve I to pressure and sequence valve I40 to exhaust. Valve I45 delivers pressure fluid through its port I38 to the left end of cylinder II5, moving piston H6 to the right. The fluid behind piston I I5 exhausts through valve I25 to return line I3I.

Piston IIB relatively rapidly swings lever II2 counterclockwise to move feed ring 40 to the'right, swinging bell cranks '55 to positively retract the tools from the work. As ring 40 reaches its limit of movement, abutment I24 kicks handle I3I to open switch I30, and pressure builds up behind piston -I I5 causing sequence valve I45 to shiftits delivery to port I42. Pressure fluid is now delivered to the right end of cylinder IIO, moving piston I09 to the left. Lever I05 moves outer collet I5 to the left to release the collet chuck from tube 25, completing the sequence.

As the reciprocable tools and tool holders are rapidly revolved around the work by .head 30, their centrifugal force is substantially balanced by the revolving counterweights .through the medium -of bell cranks 55. Consequently, the force applied to feed ring 40 need 'be only .as :much as'needed to force the carbide cutting-tips intothe work. Both the-advance andretraction of the-tools are positive, and nospringsarerelied upon.

The stationary spindle I0..gives perfect support to.rotating head 30, as .the-radial bearing is close to the tool pressure point. Additionally, the grippingactionof thecollet chuck I5--2Il takes place in alignment with bearing 28, giving -a very'rigid-support=to-tube 2501056: to the'tool .pressure point. The stationary collet '20 provides for accurate adjustment of the work to close tolerances for the cut length.

With the arrangement-of axially spaced carbide tips as shown, a sample ring is cut from the tube at the-same time as the tube is cut to proper length. Such samples,'from one or both ends of the tube,. are frequently required by purchasers. However,'the-tools'can be axially aligned and adjusted to speed thecut, and more than two toolsmay be used if necessary or desirable. The apparatuscomprises a rapid-and eflicient cut-off arrangement for cylindrical workmembers such as tubes or bars; and the operation, when initiated, is carried out inran-automaticsequence. -Also, cutting tip95 may be somounted-as to be spaced radially inwardly relative rto tip 95 so thatthe tube endis cut on beforetipJS cuts through to sever the sample ring.

While a specific embodiment of the invention has been shown and described in detail to illustrate the invention principles, it should be understood that the invention may be otherwise embodied without departing from such principles.

I claim:

1. Apparatus for effecting an annular cut in a substantially cylindrical metal member comp-rising, in combination, holding means arranged to receive and hold the member to be cut; a cutting head rotatably mounted on said holding means; mechanism operative to rotate said head; cutting means mounted for substantially radial movement on said head; mass means mounted for linear radial reciprocation on said head; linkage pivoted on said head and interconnecting said cutting means and said mass means for reversely directed radial movement on said head whereby the centrifugal forces of said cutting means and said mass means counteract each other during rotation of said head; an element movably mounted on said head and engaged with said linkage to move the latter to effect radial movement of said cutting means toward and away from the member to be cut to effect a cut in said member; and an operator connected to said element to so move the latter.

2. Apparatus for efiecting an annular cut in a substantially cylindrical metal member comprising, in combination, holding means arranged to receive and hold the member to be cut; a cutting head rotatably mounted on said holding means; mechanism operative to rotate said head; cutting means mounted for substantially radial movement on said head; mass means mounted for linear radial reciprocation on said head in axially spaced alignment with said cutting means; linkage pivoted on said head and interconnecting said cutting means and said mass means for reversely directed radial movement on said head whereby the centrifugal forces of said cutting means and said mass means counteract each other during rotation of said head; an element mounted on said head for axial movement thereon and engaged with said linkage to move the latter to effect radial movement of said cutting means toward and away from the member to be cut to effect a cut in said member; and an operator connected to said element to so move the latter.

3. Apparatus for effecting an annular cut in a substantially cylindrical metal member comprising, in combination, holding means arranged to receive and hold the member to be cut; a cutting head rotatably mounted on said holding means; mechanism operative to rotate said head; cutting means mounted for substantially radial movement on said head; mass means mounted for linear radial reciprocation on said head; linkage pivoted on said head and interconnecting said cutting means and said mass means for rever-sely directed radial movement on said head whereby the centrifugal forces of said cutting means and said mass means counteract each other during rotation of said head; an element movably mounted on said head and engaged with said linkage to move the latter to effect radial movement of said cuttin means toward and away from the member to be cut to effect a cut in said member; an operator connected to said element to so move the latter; and speed control mechanism in controlling relation with said operator and constructed and arranged to selectively control the rate of operation of said operator.

4. Apparatus for effecting an annular cut in a substantially cylindrical metal member comprising, in combination, holding means arranged to receive and hold the member to be cut; a cutting head rotatably mounted on said holding means; mechanism operative to rotate said head; cutting means mounted for substantially radial movement on said head; mass means mounted for linear radial reciprocation on said head; linkage pivoted on said head and interconnecting said cutting means and said mass means for reversely directed radial movement on said head whereby the centrifugal forces of said cutting means and said mass means counteract each other during rotation of said head; a feeding element movably mounted on said head and engaged with said linkage to move the latter to effect radial movement of said cutting means toward and away from the member to be cut to effect a cut in said member; an operator connected to said element to so move the latter; and control mechanism operatively connected to said operator and constructed and arranged to actuate the latter to move said element and including a device operable by said mechanism, at the completion of a cut to condition said mechanism to actuate said operator to move said feeding element to retract said cutting means from the work.

5. Apparatus for effecting an annular cut in a substantially cylindrical metal member comprising, in combination, holding means arranged to receive and hold the member to be out; a cutting head rotatably mounted on said holding means; mechanism operative to rotate said head; cutting means mounted for substantially radial movement on said head; mass means mounted for linear radial reciprocation on said head in axially spaced alignment with said cutting means; link means pivotally mounted on said head axially intermediate and connected to said cutting means and said mass means and oscillatable in an axial plane for effecting reversely directed radial movement of said cutting means and said mass means on said head whereby the centrifugal forces of said cutting means and said mass means counteract each other during rotation of said head; an element mounted on said head for axial movement thereon and engaged with said linkage to move the latter to effect radial movement of said cutting means toward and away from the member to be cut to effect a cut in said member; and an operator connected to said element to so move the latter.

6. Apparatus for effecting an annular cut in a substantially cylindrical metal member comprising, in combination, holding means arranged to receive and hold the member to be cut; a cutting head rotatably mounted on said holding means; mechanism operative to rotate said head; cutting means mounted for substantially radial movement on said head; mass means mounted for linear radial reciprocation on said head in axially spaced alignment with said cutting means; link means pivotally mounted on said head axially intermediate and connected to said cutting means and said mass means and oscillatable in an axial plane for effecting reversely directed radial movement of said cutting means and said mass means on said head whereby the centrifugal forces of said cutting means and said mass means counteract each other during rotation of said head; an element mounted on said head for axial movement thereon and engaged with said linkage to move the latter to effect radial movement of said cutting means toward and away from the member to be cut to effect a cut in said member; an operator connected to said element to so move the latter; and speed control mechanism in controlling relation with said operator and constructed and arranged to selectively control the rate of operation of said operator.

7. Apparatus for effecting an annular cut in a substantially cylindrical metal member comprising, in combination, holding means arranged to receive and hold the member to be cut; a cutting head rotatably mounted on said holding means; mechanism operative to rotate said head; cutting means mounted for substantially radial movement on said head; mass means mounted for linear radial reciprocation on said head in axially spaced alignment with said cutting means; link means pivotally mounted on said head axially intermediate and connected to said cutting means and said mass means and oscillatable' in an axial plane for effecting reversely directed radial movement of said cutting means and said mass means on said head whereby the centrifugal forces of said cutting means and said mass means counteract each other during rotation of said head; a feeding element mounted on said head for axial movement thereon and engaged with said linkage to move the latter to effect radial movement of said cutting means toward and away from the member to be cut to effect a cut in said member; an operator con nected to said element to so move the latter; and control mechanism operatively connected to said operator and constructed and arranged to said operator to move said feeding element to retract said cutting means from the work.

8. Apparatus for effecting an annular cut in a substantially cylindrical metal member comprising, in combination, holding means arranged to receive and hold the member to be cut; a cutting head rotatably mounted on said holding means; mechanism operative to rotate said head; cutting mean mounted for substantially radial movement on said head; mass means mounted for linear radial reciprocation on said head; linkage pivoted on said head and interconnecting said cutting means and said mass means for reversely directed radial movement on said head whereby the centrifugal forces of said cutting means and said mass means counteract each other during rotation of said head; an element movably mounted on said head and engaged with said linkage to move the latter to effect radial movement of said cutting means toward and away from the member to be cut to effect a cut in said member; an operator connected to said element to so move the latter; and control mechanism operatively connected to said operator and said holding means and including a control element manually operable to initiate operation of said control mechanism, a first actuator connected to said holding means and operatively associated with said control element, said first actuator, responsive to operation of said control element, actuating said holding means to grip the member, and a second actuator connected to said operator and operatively associated with said first actuator, said second actuator, responsive to operation of said first actuator to actuate said holding means, moving said operator to advance said cutting means toward the member to be out.

9. Apparatus for effecting an annular cut in a substantially cylindrical metal member comprising, in combination, holding means arranged to receive and hold the member to be cut; a cutting head rotatably mounted on said holding means; mechanism operative to rotate said head; cutting mean mounted for substantially radial movement on said head; mass means mounted for linear radial reciprocation on said head; linkage pivoted on said head and interconnecting said cutting means and said mass means for reversely directed radial movement on said head whereby the centrifugal forces of said cutting means and said mass means counteract each other during rotation of said head; an element movably mounted on said head and engaged with said linkage to move the latter to effect radial movement of said cutting means toward and away from the member to be cut to effect a cut in said member; an operator connected to said element to so move the latter; and control mechanism operatively connected to said operator and said holding means and including a control element manually operable to initiate operation of said control mechanism, a first actuator connected to said holding means and operatively associated withsaid control element, said first actuator, responsive to operation of said control element, actuating said holding means to grip the member, asecond actuator connected to said operator and operatively associated with said first actuator, said second actuator, responsive to operation of said first actuator to actuate said holding means, moving said operator to advance said cutting means toward the member to be cut, and adjustable control means operatively associated with said second actuator and operable thereby, after a pre-selected advance of said cuttin means, to condition said second actuator to move said operator to retract said cutting means.

10. Apparatus for effecting an annular cut in a substantially cylindrical metal member comprising, in combination, a pair of telescopically related, non-rotatable clamping means arranged to receive a member to be cut and hold the same against rotation; a cutting head rotatably mounted on said clamping means; cutting means mounted for substantially radial movement on said head; mechanism operative to rotate said head; elements rotatable with said head and movable inwardly and outwardly thereon; linkage interconnecting said cutting means and said elements for reversely related movement relative to said head whereby said elements are effective to substantially counterbalance the centrifugal force of the revolving cutting means; actuating means operative to effect relative longitudinal movement of said clamping means to grip the member to be cut; means movable axially of said head and cooperative with said linkage to advance said cutting means toward the member to effect a cut therein; means responsive to such gripping .of the member to be cut to move said axially movable means to advance said cutting means into engagement with the member at a relatively rapid rate; and feeding means operable, after the cutting means are engaged with the member, to advance the cutting means into the member at a controlled adjustable rate.

11. Apparatus for effecting an annular cut in a substantially cylindrical metal member comprising, in combination, a pair of telescopically related, non-rotatable clamping means arranged to receive a member to be cut and hold the same against rotation; a cutting head rotatably mounted on said clamping means; cutting means mounted for substantially radial movement on said head; mechanism operative to rotate said head; elements rotatable with said head and movable inwardly and outwardly thereon; linkage interconnecting said cutting means and said elements for reversely related movement relative to said head whereby said elements are effective to substantially counterbalance the centrifugal force of the revolving cutting means; actuating means operative to effect relative longitudinal movement of said clamping means to grip the member to be cut; means movable axially of said head and cooperative with said linkage to advance said cutting means toward the member to efiect a cut therein; means responsive to such gripping of the member to be cut to move said axially movable means to advance said cutting means into engagement with the member at a relatively rapid rate; feeding means operable, after the cutting means are engaged with the member, toadvance the cutting means into the member at a controlled adjustable rate; and means operable automatically in response to completion of a cut to retract said cutting means.

12. Apparatus for effecting an annular cut in a substantially cylindrical metal member comprising, in combination, holding means arranged to receive and hold the member to be cut; a cutting head rotatably mounted on said holding means; mechanism operative to rotate said head; cutting means mounted for substantially radial movement on said head; mass means mounted for linear radial reciprocation on said head; linkage pivoted on said head and interconnecting said cutting means and said mass means for reversely directed radial movement on said head whereby the centrifugal forces of said cutting means and said mass means counteract each other during rotation of said head; an element movably mounted on said head and engaged with said linkage to move the latter to effect radial movement of said cutting means toward and away from the member to be cut to effect a cut in said member; an operator connected to said element to so move the latter; and control mechanism operatively connected to said operator and said holding means and including a control element manually operable to initiate operation of said control mechanism, a first actuator connected to said holding means and operatively associated with said control element, said first actuator, responsive to operation of said control element, actuating said holding means to grip the member, a second actuator connected to said operator and operatively associated with said first actuator, said second actuator, responsive to operation of said first actuator to actuate said holding means, moving said operator to advance said cutting means toward the member to be cut at a relatively rapid rate until said cutting means engage the member to be cut, adjustable feed regulating means associated with said second actuator to control the feeding rate of said feeding means, a, device operable by said second actuator and operable thereby, when said cutting means engage the member to be cut, to condition said regulating means to regulate the rate of operation of said second actuator, and adjustable control means operatively associated with said second actuator and operable thereby, after a preselected advance of said cutting means, to condition said second actuator to move said operator to retract said cutting means, said first actuator, responsive to operation of said second actuator to retract said feeding means, operating said holding means to release the cut member.

13. Apparatus for effecting an annular cut in a substantially cylindrical metal member comprising, in combination, holding means arranged to receive and hold the member to be cut; a cutting head rotatably mounted on said holding means; mechanism operative to rotate said head; a pair of cutting means mounted for substantially radial movement on said head in axially spaced relation to each other; mass means mounted for linear radial reciprocation on said head; linkage pivoted on said head and interconnecting said cutting means and said mass means for reversely directed radial movement on said head whereby the centrifugal forces of said cutting means and said mass means counteract each other during rotation of said head; an element movably mounted on said head and engaged with said linkage to move the latter to effect radial movement of said cutting means toward and away from the member to be cut to effect a cut in said member; and an operator connected to said element to so move the latter to advance both cutting means simultaneously toward the member to be cut to effect a pair of axially spaced cuts thereon.

OLIVER A. NEALE.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,306,588 France June 10, 1919 1,592,933 Hammond et al July 20, 1926 2,018,523 Hogg Oct. 22, 1935 2,112,396 Corrigan Mar. 29, 1938 2,267,543 Watson Dec. 23, 1941 2,459,075 Hibbard Jan. 11, 1949 2,484,854 Peters Oct. 18, 1949 FOREIGN PATENTS Number Country Date 402,079 Germany Jan. 20, 1924 

